Vehicle



A. M. WOLF VEHICLE April 18, 1939.

Filed Sept. 25, 1935 5 Sheets-Sheet l W .w M

April 18, 1939. A M. WOLF 2,155,287

' VEHI CLE Filed Sept. 25, 1935 5 Sheets-Sheet 2 INVENTOR April 13, 1939. A. M. WOLF 8 VEHICLE Filed Sept. 25, 1935 5 Sheets-Sheet 5 INVENTOR April 18, 1939.

A. M. WOLF VEHICLE Filed Sept. 25. 1955 5 Sheets-Sheet v INVENTQR dog P 1939- Q A. M. WOLF 2,155,287

VEHICLE 7 Filed Sept 25, 1935 5 Sheets-Sheet 5 INVENTOR Patented Apr. 18, 1939 UNITED STATES PATENT OFFICE v VEHICLE Austin M. Wolf, Plainfield, N. J. Application September 25, 1935, Serial No. 41,958 9 Claims. (01. 180-54) This invention relates to motor vehicles and has for one of its objects to provide a simple and compact arrangement of the motor transmission mechanism and clutch in combination with an 5 accessory, such as a compressor, having driving connection between the clutch and transmission, and means responsive to clutch operation for rendering said accessory functionally ineffective. It is another object of the invention to provide 10 a cooling system in which the radiator is positioned in parallel relation with the motor crank shaft and an air circulating fan associated therewith and having driving connection with one end of the crank shaft, while a second fan has a 15 driving connection with the other end of the crank shaft and operates to create a circulation of air longitudinally of the motor.

The invention in one of its embodiments relates in particular to dual powered motor buses in ;n which a common radiator is provided for a pair of prime movers, together with means operatively connected with each of the prime movers for circulating air through said radiator.

Another object of the invention is to provide a power transmission means which is common to both of the prime movers having a single power input shaft and an air circulating fan coupled to one end of said shaft.

Still further objects of the invention will appear as a description thereof proceeds, with reference to accompanying drawings in which:

Fig. 1 is a plan view showing the general disposition of the elements comprising the vehicle. Fig. 2 is a side elevation thereof. 35 Fig. 3 is an elevation of the power plant, the

driving axle and the correlating parts.

Fig. 3A shows the support for the power plant at the trunnion end of the engine.

Figs. 4, 5 and 6 are detailed views showing a 40 portion of the power plant mounting.

Fig. '1 is a sectional view of the transfer case showing the general disposition of the gearing,

accessory drives, engine and transmission mountin'gs and a portion of the clutch operating mecha- 5 nism. This view also illustrates my proposed ventilating system of the clutch compartment.

Figs. 8 and 9 show the clutch synchronizing mechanism.

Fig. 10 is a plan view illustrating mechanism 5 for locking out one of the clutches and rendering one prime mover or motor inoperative.

Referring to Figs. 1 and 2 the vehicle illustrated is that of a bus in which the chassis frame and body frame are combined into the unitary structure. The main rail members and 2form a foundation for the body structure 3 by means of cross channels 5, 6, 1, 8, 9 and II]. There are other supporting members, not shown, to support the body, particularly the portion to the rear of cross member ID in which a partial cantilever effect is obtained for the overhanging portion of the body which is furthermore braced in position by that portion to the rear of door l5 by means of the vertical posts I6, the roof structure l1 and the belt rail I8.

A front door 25 is located ahead of the front wheel house 26 and the door I5 is shown ahead of the rear wheel house 21.

The main rails and 2 are tied together by the front cross member 38 and the cross mem bers 3|, 32, 33, 34 and 35. The front axle 4|] is provided with the wheels 4| and 42. The driving axle 45 is provided with the dual wheel 46 and 41.

Above cross members 6, 1, 8 and 9 is located. the flooring 50. At the forward end of same is located the drivers seat, not shown, behind the steering wheel 5|. The steering gear mechanism within the housing 52 actuates the drag link 53 which is attached to the steering arm 54 on the front axle 40.' The cross tie rod 55 connects the arms 56 and 51 to the front wheel spindles.

The forward end of flooring 50 is extended in the form of a ramp or toe board 66 which acts as a support for the drivers feet and through which extend pedals 6| and 62, these being the brake and clutch pedals respectively. They are mounted on tube 63 and shaft 64 which are properly mounted on the frame structure. They actuate the control valves 65 and. 66 through the intermediary of rods 61 and 68. The control valves 65 and 66 are shown mounted oncross member 32 and their function will be described later.

The front axle takes the forward body load through the front springs 1| and 12 which are 40 heldto the frame by brackets 13, 14, 15, 16, brackets 13 and 15 taking the eyes of the springs directly, whereas brackets 14 and 16 connect the springs to the frame through the customary shackle connection. 5

' The driving axle takes the rear portion of the body load by means of springs 6| and 82. Brackets 83 and 84 transfer the frame load to spring 8| and brackets 85 and 86 transfer the load to spring 82. Brackets 83 and 85 take the eye 5 ends of the rear springs, whereas brackets 84 and 86 are of the slipper type and takethe open ends of the rear springs. It will be noted that the main rails and 2 have a kick-up over the driving axle and sweep downward toward the rear terminating at the brackets 9| and 92, the latter forming the extension of the main rails to act as a power plant support.

Rearwardly of door I-the floor 59 continues in the ramp section 95 in order to provide riding clearance for the driving axle and continues to the rear of same in the horizontal floor portion 96. The rear seat cushion 98 and the seat back 99 are located over the box I99 which houses the engine or engines. This box has a vertical wall I9I and the top wall I92. These walls together with the wall I3 hermetically seal the engine compartment from the interior of the vehicle, to prevent any ingress of fumes.

The power plant consists of the-prime movers I95 and I96 which are united to the'transfer case II9. To the latter is secured the transmission III. Power is conveyed therefrom to driving axle 45 by means of propeller shaft II5 with the slip type universal joint II6 adjacent the transmission and the universal joint II1 adjacent the driving axle. The hand brake disc I29 is located on joint II6.

In axial, alignment with the main shaft of transmission III is the cooling fan I25 which directs a blast of air rearwardly through the core of the radiator I26. To the outer end of the crank shaft of each of the prime movers I95, I96 a fan I25 is operatively connected for the purpose of creating a continuous circulation of air longitudinally over and around the respective prime movers.

The gasoline tank I39 is located amidships and is provided with the filler I3I which is connected to the tank by means of a flexible tubing I32.

The braking system is of the conventional compressed air type with .the actuating diaphragms I35 and I36 on front axle 49 and diaphragms I31 and I38 on the driving axle 45. The compressor I49 is driven by the power plant and air stored in the reservoirs MI. The piping between compressor I49 and the reservoirs MI is not shown since it is well known in the art as well as the ,piping from the reservoirs I4I to the control valve 65 from whence piping, not shown, conveys air to the diaphragms I35, I36, I31 and I38.

Referring to Fig. 3 it will be noted that the frame extension 92 forms one-half of a circular bracket, the other half being the cap I 45. Fig. 4 is a plan view of the rear end of rails I and 2 showing the extensions 9| and 92 with their caps I44 and I45 respectively. The bell-housings I59 and I5I of engines I95 and I96are provided on each side with bosses I52, I53 and I54, I55 respectively. Again referring to Figs. 1,2 8, and 4, the bell-housings I59 and I5I are supported on brackets I58 and I59, the plan view of which is clearly shown in Fig. 4. The bosses I6,I,"'162,' I63 and I64 of these brackets take the bosses I52, I53, I54 and I55 of bell-housings I59 and I5I respectively. Brackets I58 and I 59 are welded to the cross tube I69. The latter is sup ported by brackets 9I. and 92 through the intermediary of rubber bushings.

Fig. 5 is a section on line 5-5 of Fig.1 4 through bracket 92 "and its cap I45. 'Between same and tube I 69 are located the rubber walls I66. One such wall is shown in its natural or flat state in Fig. 6. As an example, should it be desired to press the iwallto a final thickness of /2" when cap I45 is drawn up tightly to bracket 92, the

thickness of the rubber could be made s i ly oversize such as The extent of the'oversize to the crankshaft centre.

will depend upon the durometer reading of the rubber. In assembling tube I69 in the brackets 9 I and 92 a wall of rubber I66 is placed in bracket 92, being curved to conform to the general shape of the bracket, Tube I89 is then laid inside of the rubber, a second wall I66 is laid over tube I69 and curved around the latter by pressing cap I45 as close to bracket 92 as is permissible. The cap screws 119 in Fig. 3 are then drawn up, compressing the rubber walls I66. The length of the wall I68 in Fig. 6 is less than the mean radius of the wall in Fig. 5 in order 'to allow overflow of the rubber under compression. In the same manner the width of the rubber is slightly less than the width of either bracket 9I or 92 in an axial direction in relation to tube I 69. In order to prevent the flow of rubber into the space between cap I46 and bracket 92 as the former is.-

drawn up; the thin metallic shims I12 and I13 are inserted before the compression process. They bridge the gap then existent and as the bracket parts are drawn together they prevent the flow of rubber radially outward.

The starting crank ends' of engines I95 and I96 are provided with the customary trunnions I15 and I16 respectively. Brackets I 18 and I19 encompass these trunnions and extend downward to form feet I89, as shown in Fig. 3A. The-feet rest upon the brackets. I8I-and I82 which are welded to tube I69 near its extremities. The distance from the center of the engine crankshaft to the face of brackets II and I 82 is the same as the distance to the horizontal face of the lugs I52 and I53, I54, and I55 of the bellhousings I 59 and I5I respectively where they rest upon the brackets I58 and I59. .In this manner it is possible to place the brackets I58, I59, I8I and I82 on tube I69 and align their faces on a face-plate after which the welding operation ensues. This insures perfect alignment of the brackets and the proper aligned support of the engines through their 'outer supports I18 and I19 and their bell-housings I59 and I5I.

It willbe noted in Figs. 2 and 3 that the tube I69 is not located below the engine crankshaft center but to the right thereof. The center of tube I69 is so located that it is below the center gravity of the complete power plant including engines I95 and I96, the clutches and mechasince the engines are alike and their disposition symmetrical about the longitudinal centre of the vehicle, their cetre of gravity would balance at the centre on the crankshaft axis. This leaves theweight of the transmission II I and universal joint II6 as arroverhanging static load in respect Tube I69 is therefore located unden'the centre gravity of the entire unit and provides a two 'point mounting of the entire power plant by means of brackets 9| and I 92. When accelerating or decelerating the vehicle there will be a natural tendency of the centre gravity/to rotate about the centre of tube I69 and the frictional grip of the rubber mountings in brackets SI and 92 would be insuficient to .sion III in order to clear same when it is retransmission. Bracket I90 has an extension lo-- cated between the rubber blocks I90 and I92. The iatter is located between the frame, cross member 35'and bracket I90. The former extendsbetween bracket I90 and a washer under. the head of bolt I93 which passes through blocks- I9I and I92, bracket I90 and cross member 35.

The desired resiliency of blocks I M and I92 is obtained by the extent of vtheir compression by bolt I93, which compression is made sufllcient to snub incipient rotational tendencies of the power plant when a rocking action is instituted.

The power plant suspension system, while of a three point type, is essentially a two point mounting except when extraneous forces bring the third point into. effect. Since all points are of rubber, any distortion between the frame rails I and 2 and between which the cross member 35 is mounted, the rubber compensates for any misalignment as well as forming a noise insulating medium between the power plant and the frame base. Cross member 35 is bolted to main rails I and 2 so that it can be removed when it is desirable to take out the transmission III and leave the remainder of the power plant in position.

In Figs. 1 and 3 it will be noted. that the frame cross member I0 extends slightly below transmismoved. In extending outwardly from the centre it is curved upwardly to contact with the under side of rails I and 2, thereby tying them together in addition to cross member 35. They extend outwardly to form a rear support for the base of the body structure 20I and 202. The front of the seat box IN is extended down to the level of the rails land 2 in order to give structural stability at this point. Angle irons 205 and 206 also brace the frame structure and are welded to the cross angle 201 in Fig. 3, which supports plate 91 which is a continuation of the flooring 96. Plate 91 is used in order'to give clearance for the, control head 2I0 of transmission III. f

The horizontal section through the transfer ,case is shown in Fig. '7. The bell-housing I ofce engine I05 appears in the lower portion of the view. Bell-housing I5I of engine I06, not

4 shown, is symmetrically located at the other side of the longitudinal centre line. Within the transfer case H0 is located the gearing whereby the power output of the two engines is delivered to the transmission II I which bolts against the flange 220 of the transfer case I I0 being held thereto by means of the studs shown. A conventional clutch 225 is mounted in the flywheel within bell housing I50 and a similar clutch mechanism is incorporated in the opposite engine. A bevel gear 228 is integral with the clutch shaft 229. The corresponding gear 230 is also integral with the clutch shaft 23I. Referring to the latter unit, it will be seen that it is mounted in a large double row ball-bearing 232 which is located between a shoulder and gear 230 and-the lock nut 232'. This bearing is nested in the carrier 234 and prevented from end movement by a shoulder within same and the clutch throw-out sleeve member 235. {The end surface of the sleeve extension is provided with a threaded section 236 which will return through holes 238 any oil that might seep through and by the bearing 232. Only one oil hole 238 is shown; whereas three are actually used and they empty into the counterbore 239; thence the oil returns to the sump 24I in Fig. 3.

Vertical clutch throw-out shafts 244 and 245 are provided to actuate each clutch independently- Keyed to these shafts are the yokes 246 and 241 which terminate in the bosses 248 and 249 respectively. It is of course understood that a similar arm extends above the shaft centre as well as the arm shown below in Fig. 8. Within the bosses 248 and 249 are mounted a swiveling member 252, which is shown in the lower yoke in the view, the upper yoke receiving a like member. The swiveling member 252 has a square portion 253 which abuts a lug 254 on the throwout cage 255. The lug 254 receives the necessary thrust to throw out the clutch when the yoke 246 is moved in a clockwise direction of rotation. The other clutch is thrown out in similar fashion when the yoke 241 is moved in a counterclockwise rotation. Within the cage 255 is located the 'antifriction throw-out bearing 256. The outer race of this bearing normally clears flange 260 of the clutch throw-out sleeve 26I when'the clutch The gear 228, its bearing, carrier, and the clutch sleeve form a unit which is assembled before inserting into the transfer case I I0. Proper positioning of this unit is made possible by means of a laminated shim or a series of shims 261. It. will be apparent that the outside diameter of the centralizing cylindrical portion of carrier 234 in case I I0 is slightly larger than the maximum diameter of gear 228in order to permit of assembly or disassembly of the entire unit.

Gears 228 and 230 mesh with the gear 210 which has a sleeve extension 21I which is in turn supported by the anti-friction bearings 212 and 213. The latter are mounted within the carrier 214. The latter is guided within a cylindricalsection of case H0 and proper meshing of gear 210 with gears 228 and 230 is obtainable by means of shims 218. Within the sleeve portion 280 which projects toward the cone centre of the gear and also within the web portion of. the gear,

there are machined the internal splines 28I.

which fit the external splines 282 of the clutch shaft 285 of transmission III. The shaft 285 is a standard clutch shaft of a transmission used for unit power plant mounting in which case the splines 282 would receive the splined clutch driven hub. In my invention the design of the various parts is such that a standard transmission is used without resorting to any special parts or machined fits. For ordinary unit power plant use the transmission III is bolted to the clutch housing interposed between the transmission and the bell-housing ofthe engine. In my case the flange 220 of transfer case H0 is so located and machined as to take the' transmission I II and to position the splines 282 in order that the power transmitted to gear 210 can be transferred to the standard shaft 285 and thence into thetransmission in the usual way. The end cap 286 of transmission III retains the constant mesh gear bearing 281 in place and also centers the transmission clutch shaft by piloting within the machined flange 288 of the transfer case. The bolt holes that are normally in the end wall of the regular clutch housing are. located in flange 220 so that the retention and mounting of transmission I I I is the same as the normal incorporation of transmission III in the conventional unit power plant. It would be apparent;

that with the standard clutch shaft 285 in various capacity transmissions and with the standard mounting flange 220 that various transmissions can be bolted to the case IIO. can also be bolted to the bell-housings I50 and II if they are kept to standard dimensions. The customary clutch housing flange in the ordinary unit powerplant has its counterpart in the flange 290 of case H0.

The clutch shaft 285 is provided at the left extremity with the extension or pilot 284 which in the conventional unit power plant is piloted in the clutch throw-out bearing within the engine flywheel. The shaft 285 is thus centered by the pilot 294 and the bearing 281 in the transmission case. In order to maintain shaft 285 in its proper centralized position and not depend upon the fit of splines I8I and I82 for this purpose, since there is a clearance fit between them, the centering member 295 is pressed on the hub 280 and its internally ground hole fits on the outside diameter of splines 282. The seat for the centering member 295 is machined on hub 280 at the same time that thefaces on sleeve 21I are machined for the bearings 212 and 213, thereby establishing concentricity of all these members as well as the gear itself. Whereas splines 28I and 282 have a sliding flt, it would be possible to make them a permanent fit, but this would prevent ready insertion of shaft 285 or its removal with the transmission I I i when the latter is taken out in servicing. Furthermore, more precise concentric relationship can be obtained by the method shown than by counting upon the proper splined fit.

A further advantage is taken of thesplines 282 by designing the various parts so that they will project beyond the centralizing member 295 as shown. This is furthermore necessary since the hub 280 cannot extend any more to theleft than is permissible in the machining of the teeth of the gear in order that the hub 280 remain within the base cone angle in order to provide clearance of the gear generating machinery. The projecting portions of splines 282 mate with the internal splined portion of hub 298 which is mounted on the fan drive shaft 299. The right end of the latter is machined out to accurately fit over the pilot 294. This fit assures running concentricity of the right end of shaft 299. The left end thereof is supported in the anti-friction bearing 300' which is housed within the transfer case cover 30I. The lock nut 302 holds bearing 300 against a shoulder on shaft 299. :The seal 303 within the end ;cap 304 prevents leakage of lubricant from the transfer case H0. Fan I25 is mounted on shaft 299\ through the intermediary of the 35 hub 306.

It will be apparent that in assembling the gearing, the gear 210, its bearings 212 and 213, the

carrier 214, shims 218 and the centering member 1 295 are inserted through the opening provided by 0 he cover 30I and set into place. Thereafter'the gear units 228 and 230are inserted from their respective ends of the transfer case.

In order to provide ample cooling-within the clutch housing and thereby dissipate the accumulated heat obtained and stored in the members Various engines tube 308. A screened opening 3I0 is provided in transfer case II 0 or any other desirable part wherein the clutch and flywheel are housed permitting ingress of outside cool air. provide a drive for an air compressor a sprocket 3I2 is piloted into an internal hole in the right end of sleeve 21I. The pin 3I3, same being one of several used, transmits the necessary driving torque from sleeve 21I to sprocket 3I2. locking nut 3I4 for bearing 213 encompasses pin 3I3 when the former is in its properposition. To remove sprocket 3I2, the locking nut 3 is screwed to the right whereby pin 3I3 is accessible for driving through to the interior of sleeve 21I when the transmission and its clutch shaft 285 have been withdrawn from the interior of sleeve 21I, It will be, seen that sprocket 3I2 becomes an additional element in the unit taking in the gear 210, its bearings, carrier andcentering ,sump 24I to communicate with chamber 3| lot the transfer case IIO providing lubricant for the air compressor driving mechanism, including sprockets and chain,

, The use of multiple engines requires positive synchronization of the clutches when they engage. While it is theoretically possible to make a manual adjustment, same cannot last since any unequal wear in the clutch facings of one clutch as against the other, will immediately throw the clutches, out of step. In my invention I have provided a means to accurately synchronize clutch engagement regardless of manual adjust! ment or the condition of the clutches themselves or the friction in their operating mechanism. The method pursued is to throw out'the clutches at the same instant so that their following engagement must necessarily be simultaneous. While I show clutch actuation by means of fluid pressure, it is also evident that the same principle can be used by the use of mechanical means. In Fig. 1 the brake pedal IiI controls the valve 65. The pipe previously mentioned that conveys compressed air from the reservoir I4I to the brake valve 65 also conveys airto clutch control valve 66, which is actuated by pedal 62. Piping runs from this valve to the clutch actuating cylinder 320 which is mounted on top of transfer case I I0 and adjacent compressor I40. Referring to Figs. 8 and 9 it will be noted that a piston 32I is located within the cylinder 320 and normally kept in the position shown by means of the spring 322 which bears against piston 32I at its right end and the end cap 323 on the left; When air is admitted from the valve 66 to the actuating cylinder 320 it enters through the opening 324 and moves piston 32I toward the left, compressing spring 322, while the piston rod 325 moves with it, Secured to the hollow left end of piston rod 325 is secured the shoe 330 and the stem 33I. The

latter is provided with a shoulder 332 against" which abuts the spring 333-which bears against In order to end of stem 33! and is prevented from moving beyond the position shown under spring pressure by abutting cap screw head 335. Relative movement of block 334 to the right in relation to stem 33l is permissible by compression of spring 333. The equalizer 338 has a rectangular hub extension 339 which is pivotally mounted on block 334 by means of pins 34l and 342, These pins are anchored in block 334 and terminate as shown in Fig. 9 so as to clear stem 334. The exterior of block 334 is rectangular in cross section but the top and bottom surfaces as shown in Fig. 8 are inclined, the purpose of which will be shortly described.

Equalizer 330 is provided with hardened but tons 345 and 346 which contact during clutch actuation with the rounded ends of set screws 341 and 348. These screws are adjustable and are provided with lock nuts in the customary manner. The former is mounted on the offset lever 35! having the hub 352 which is keyed to the clutch throw-out shaft 294. The screw 348 is mounted in the lever 355 having hub 356 and from which extends lever arm 351, thus forming the bell crank 355351. The hub 356 is Drovided with the bushing 358 so that it may freely rotate axially about throw-out shaft 244. A lever 360, in Fig. 9 is keyed to the left throwout shaft 245 and an adustable rod 362 with the necessary yoke ends, one being fixed and the other adjustable, connects it with lever 351. It will therefore be seen that the clutch throwout shafts 244 and 245 will be actuated when piston 325 and the equalizer 338 move to the left in Fig. 8. The rlrst movement of piston 325 results first in the take-up of any clearance between button 345 and screw 341 and between button 346 and screw 348. Further movement to the left, due to the pivotal relationship of equalizer 338 on block 334 results in the taking up of the'clearance between the outer race of the clutch throw-out bearing 256 and the clutch sleeve 260 in Fig. '7. During this movement, equalizer 338 clears the inside curved surface of shoe 330 due to the pressure of spring 333. The latter is sufficiently strong to overcome'any frictional resistance of pivots. shafts and levers up to the point of attempting to actuate the clutch sleeve 260. It will be seen that up to this point the action is completely equalized and that both throw-out bearings come in contact with the clutch throw-out sleeves and are ready to move them at the same instant due to the equalizing action of element 338. Further movement of piston rod 325 to the left causes compression of spring 333, whereby the equalizer 338 is caused to stand still while stem 33! and the equalizer shoe 330 advance to take up the clearance between the latter and equalizer 338, this terminating in their frictional contact. The curved surface of equalizer 338 is machined to the same radius as the inside of shoe 330 insuring intimate contact between them. The reason that equalizer 338 is retardedin its movement is due to the fact that clutch spring 262 of each clutch causes suflicient resistance to make spring 333 compress. This is readily understood when it is mentioned that clutch spring 262 has an approximate pressure of 400 lbs. The compression of the clutch springs 262 is brought about after contact between shoe 330 and equalizer 338, at which time further .movement of piston rod 325 to the left causes 'shoe 330 and equalizer 338, these two units now and piston 32l and its piston 325 move to the right. The rigid relationship exists up to the time that the outer races of release bearings 256 are ready to depart from the faces of sleeves 266. Further movement of piston rod 325 to the right permits the shoe 330 to separate from equalizer 338 under the influence of spring 333. The entire assembly will thus assume the position shown in Fig. 8 where it is ready for a further release action. In order to prevent excessive movement of piston 32I so that throw-out bearing 256 be not unduly loaded, a stop screw 365 is located in the stirrup 366 surrounding the equalizer mechanism and attached to cylinder cap 323 by means of feet 366 and 361. In order to prevent rotational movement of the unit, since there is no restraining influence on piston 32l, pin 34| of the equalizer hub 339 extends in a slot in stirrup 366. The rotational movement of the shoe 330 is prevented by means of fingers 310 and 31! which act as a side guide on the end of the curved rim of equalizer 338. In this way the entire mechanism is kept in proper alignment.

It is essential that with multiple engines the clutches engage simultaneously. In the. above mentioned mechanism it will be noted that regardless of variation and friction of the operating mechanism, the moment of movement of the clutch sleeve 260 is absolutely synchronized. Since the clutches disengage at the same instant and at which time the entire mechanism is locked solid, the clutches must engage simultaneously during the reverse movement of the-mechanism. It will be noted that before each disengagement the equalizing mechanism takes feel of the two distinct clutch throw-out mechanisms and at the proper time the mechanism is locked solid. In

this way every clutch actuation amounts to an I individual'and distinct adjustment prior to the operation. This is entirely apart from a predetermined mechanism set-up which cannot sense any unusual variations following the initial adjustment. The only possible variation in clutch synchronization taking in both disengagement and engagement would be with a variation in the pressure in the individual clutch springs 262. These springs are manufactured to very close limits and if necessary can be selected so that the variation between them is nil, thus assuring positive synchronization of clutch action. It was noted in reference to Figs. 3 and '1 that the air compressor was driven from sprocket 3 I 2 attached to the driven gear sleeve 21L Since this drive occurs between the clutch or clutches and the transmission mechanism, operation of the compressor during the moment of disengaging the clutch or clutches would cause retardation of this immediate mechanism due to the resistance of the compressor. Such slowing up would cause improper gear shifting and in order to overcome such an occurrence a bell crank 314 is pivotedon fulcrum 315, contacting at one end with the shoe 330 and at the'opposite end with the stem 311 of compressor I40. The lower end of the latter just clears the inlet valve 318, same being shown as of the spring or disc type. In order to prevent the compressor I40 from operating during clutch actuation, movement of piston 32| to the left will cause depression of stem 311 and thus hold open valve 318 preventing the compressor from functioning but merely idling over under atmospheric pressure with the inertia or flywheel effect of its parts and drive as well as that of fan I25 and its drive. Stem 311 can be made to function with the usual compressor unloader mechanism. If so desired, a set screw can be located at the end of depending arm of hell crank 314 to contact with shoe 330. It is to be noted that the latter moves in com'unction with piston 32l for each clutch actuation. While I have shown a. fluid operating mechanism to actuatethe rod 325, it will be'readily understood that same can be mechanically actuated from the clutch pedal 62 in Fig. 1, if so desired.

I propose to latch out e'itherone of the two engines and a means of so doing is accomplished in Fig. 10. It will be noted that the clutch throwout shafts 244 and 245 extend through the bottom of the transfer case H as indicated in Fig. 3 andshown diagrammatically in Fig. 10. To the shafts are affixed the levers 393 and 399 having a forked end and a spherical depression into which can be fitted a spherical base of wing nut 40l on the rod 402 which is pivoted below the transfer case on fulcrum 403. The left clutch is diagrammatically shown latched out. This operation is performed by throwing out the clutches which causes clockwise rotation on lever 398 and counterclockwise rotation on lever 399. With the clutches so set, the rod 402 is swung to the left and wing nut 40l run-up on the rod until its 399. The left clutch is then held in the disengaged position by yoke 241 of Fig. '7 and gear 230 will rotate idly as will the clutch disc in driving connection with the end thereof. The clutch plate having been released and being held there, there is no frictional engagement of the clutch. Similar operation can be made upon the right clutch by means of holding lever 398 in a disengaged position. v

When one of the clutches is latched out, the equalizing mechanism will be affected unless special provisions are taken care of so that the actuation of the working clutch will be normal.

This can be accomplished by locking equalizer 338 in Fig. 8 when one of the clutches is latched spherical end seats in the spherical cavity of lever out. In order to avoidthe use. of extra parts;

the construction shown has been evolved to automatically take care of such a situation. It will be noted that block 334 has a tapered top and bottom surface. The hole inthe hub 339 of equalizer 338 is rectangular in shape and its height is slightly greater than the greatest vertical thickness of block 334' so that the rocking of equalizer 338 about pins 3 and 342 be unimpeded. For the purpose of explanation, let it be considered that lever 35! has been moved to theleft in Fig.3 through the looking out of the v clutch controlled by. clutch shaft 244. Movement of piston 32l to the left for actuation ,ofthe s01e working clutch would cause counterclockwise rotation of equalizer 333 as it advances with stem 33L This is due to contact of button 34$ against screw 314. This movement is, however, only slight, since the bottom surface of the rectangular hole in hub 399 will contact with the bottom-.tapered surface of block 334. At this point the equalizer 338 can rock no further and to all intent is a solid unit in the entire as I sembly. Lever 355 and clutch shaft 245 are now sv actuated upon further movement of piston 32L The operation in the case of the latching out of the other engine would following in similar fash-' ion as explained above excepting that equalizer 338-would be imparted a slight rotation'in a clockwise direction when button 345 first {contacts with screw 341, screw 348 being out of operating distance at this'time. r

The frictional contact established between equalizer 338 and shoe 330 will depend upon the area and the materials of the contacting surfaces. Naturally, they are made sufficien-t to prevent rotation of equalizer 338 when the clutches are being actuated, in disengagement or engagement. The forces of the clutch springs 262 and the leverages involved from either-clutch throw-out shaft (both being preferably alikel to the pivotal axis of pins 3 and 342 and iii- 4 cluding the radius of the frictional contacting surfaces on 330 and 338, are all taken into acjf count so that the frictional grip of the relating members will not be impaired. It is uesname to'use relatively-soft metallicsurfaces as I bronze for shoe 330 and an aluminum alloy for equalizer 338. It will be readily seen that other variations are possible in the utilization of soft metal such as' lead with another metal; It is even possible to line one of the curvedsurfaces with a material similar to brake lining or one possessing resiliency such as a rubber compound. Furthermore, it is possible to change the physical surface of shoe 330 and equalizer 338 by means of rough machining or by the machining and both engines running, the primary circuit of the ignition system'for each engine is completed. When rod 402 has been swung to the left as indicated diagrammatically, switch'4l0 breaks the primary circuit for the engine on that side of the vehicle, while switch 409 maintains the circuit intact for the right engine. Conversely, if rod 402 is swung to the rightin the position for latchingv out clutch shaft'24'4,

switch 409 breaks the contact in the primary M circuit for the right engine and maintainsjti in switch 0 for the left engine. Link 4l2ektends to the left from rod 406 and is secured Itofthe lever 4| 3 of theair valve 4l4 In the neutral position shown, air entering pipe '4l5 "passes through the barrel of valve 4 without 'restriction'and enters pipe 6 to be conveyedftdthe clutch control cylinder 320. When rod 402 is swung eitherto the right or left to cut out an engine, the barrel of valve 4 is rotatedaxially and therefore its through-passage restricts the flow through the inlet and, outlet ports 'ofjvalve 4 cutting down the effective area of the valve capacity. This throttling effectwill then reduce the pressure in cylinder 320for clutchadtuation when only one engine is running. 'Th 'evclu t'ch spring pressure is in the neighborhood Q I .400 lbs; same has only to be overcome whe'nfone engine is used. as compared to 800. lbs. when both engines are in action.

From the above description it I have provided a very simple and compact arrangement of the motor transmission and clutch will b seen that,

together with a compressor or other accessory and means whereby the accessory is operatively disconnected during clutch operation so as to relieve the clutch operating mechanism of the resistance of the compressor. This is a very desirable feature, particularly in connection with the operation of dual powered motor buses Further it will be seen that I provide a very eflicient cooling system in which cooling blasts of air are circulated longitudinally over the motors or prime movers in addition to the circulation of air through the water cooling radiator. By providinga common transmission mechanism for the two prime movers, with said mechanism and a coupling between'the radiator fan and the power input shaft enclosed within a common housing, as shown in Fig. '7, I have materially simplified and increased the efficient and reliable operation of mechanism of this character as hereto fore used in the art.

In the foregoing description and embodiments of my present improvements, which are believed to exemplify the most practical means for accomplishing the ends in view. Nevertheless it is of courseto be understood that the essential features of the invention might also be incorporated in various other alternative mechanical structures and I accordingly reserve the aoflprivilege of resorting to all such variations, and

, accessory driving mechanism between said clutch and transmission, an accessory driven thereby, an interconnecting element between said clutch operating means and said accessory, and means for interrupting the operation of said accessory during clutch operation through said interconnecting element. w

2. In a vehicle, a pair of prime movers located transversely at an extremity of the vehicle, clutches for said prime movers, means for operating one or both of said clutches, means for locking out either one of said clutches, a central transfer case, a transmission attached to said transfer case, a driving axle, and power transmitting mechanism between said transmission and said driving axle.

the accompanying drawings I have disclosed mechanical 3. In combination, a prime mover, a transmission, a clutch between said prime mover and nection between the' cliitch and transmission,

clutch operating means, and means responsive, to clutch operation for rendering said accessory functionally ineffective.

'5. In combination, a prime mover having a crank-shaft, a cooling system including a radiator positioned in parallel relation to said crank-shaft, a fan associated with said radiator and having a driving connection with one end of said crankshaft, and a second fan having a driving connection with the other end of said crank-shaftand positioned in a plane at substantially right angles thereto, to create a circulation of air longitudinally of the prime mover.

6. In combination, a pair of prime movers, a common-radiator therefor, power transfer gearing, a shaft driven thereby, a common housing for said gearing and shaft, and a fan directly connected to and driven by said shaft for circulating ,air through said radiator.

7. In combination, a pair of prime movers ar- 7 ranged in alignment and each having a crankshaft, 9. common radiator for said prime movers positioned in parallel relation to said crankshafts and laterally spaced therefrom, power transfer gearing between the prime-movers and means for connecting said gearing with the crank-shafts, and a fan driten by said gearing for circulating air through said radiator.

8. In combination, a pair of prime movers, a

common radiator therefor, an air circulating fan both prime movers, including a single power ,-I

input shaft, and coupling means between one end of said shaft and the fan driving shaft.

AUSTIN M. WOLF. 

